JP3083771B2 - Diaphragm pump with at least one stroke piston - Google Patents

Abstract

The annular space (9) within the nonrotating housing (10) stands concentric to the rotation axis of (8) of the cam (6) or crank in pump runs and (9) contains two balls (12) to ride freely round the inside surface (13) of the space (9). The remainder of the space (9) lies empty and free of fluid, using a radial width of space slightly exceeding that of the balls in this direction so that the disbalance as the pump starts moves the balls between the inner and outer walls of the space (9) with the result that sliding friction between balls and between balls and the space limits (9) entrains the balls peripherally as pump starts. The circular groove forming the space (9) has its own releasable cover (15), with space radial width 1/10 to 1/4 mm greater than maximum ball (12) diameter. The outer space wall (13) as ball track runs straight axi-parallel and normal to the largest diameter and thus forms a hollow cylinder of refined steel or hard chromeplated surfaces. The balls are identical in mass and dimension. A permanently fitted counterweight (7) on the housing (10) containing the ring groove (9) faces away from the eccentric part of the cam (6) and/or the connecting rod (5).

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a diaphragm pump having at least one diaphragm and a stroke piston attached to the diaphragm, wherein a connecting rod is engaged with the stroke piston, and the connecting rod is connected to the stroke piston. At the opposite end, it is adapted to be driven by a load by an eccentric or a crankshaft, and at least a part of the rotating oscillating mass is arranged opposite to the oscillating mass and is rigidly attached to the oscillating mass. Of the type mounted and compensated by at least one opposing weight or mass that moves synchronously with the oscillating mass.

[0002]

BACKGROUND OF THE INVENTION Diaphragm pumps are known in various shapes and sizes. By means of the crankshaft or the eccentric, the mass which can move from the center outward and transversely to the rotation, i.e. the rotational and oscillating mass, is compensated by a rigidly mounted, synchronously moving counter mass.

[0003] Despite the fact that the mass compensation is performed very carefully, vibrations are not excluded. In particular, in the case of diaphragm pumps, a change in force is caused by the respective discharge medium, depending on the counter pressure (Gegendruck) which also occurs or according to the discharge rate and / or the number of revolutions of the diaphragm pump.

[0004] In a diaphragm pump, a special condition (V
erhaeltnisse), since the piston movement is hindered to some extent by the diaphragm and is affected anyway. The diaphragm movement is influenced not only by the connecting rod, but also on the one hand by the fluctuating or different pressures and on the other hand by the fluctuating or different negative pressure, which means that the reaction force ( Reaktionskraft), which in turn causes additional unforeseeable imbalance. In the case of diaphragm pumps of normal speed, the conditions change very rapidly, in particular on discharge or suction of gaseous media, so that unforeseeable imbalances also change size very rapidly.

[0005]

SUMMARY OF THE INVENTION The object of the invention is to improve a diaphragm pump of the type mentioned at the outset in such a way that the changing forces, in particular the reaction force generated by the discharge medium, are almost automatically compensated for in the diaphragm. It is to be. In this case, it is desired that the compensation of the force be effected quickly and finely at the start of the diaphragm pump or shortly thereafter.

[0006]

In order to solve the above-mentioned problems, according to the present invention, an eccentric body or a ring-shaped hollow chamber coaxially with the rotation axis of a crankshaft is provided inside a casing or casing part which rotates together. Are located in
At least two roller members are arranged in the hollow chamber,
The roller member rolls freely on the inner surface of the outer peripheral portion of the hollow chamber, and the inside of the ring-shaped hollow chamber is empty except for the roller member, and is in a state without liquid, and the ring-shaped The radial width of the cavity is slightly greater than the radial diameter of the roller members, and the roller members may be unbalanced during start-up due to the outer restriction or the wall and inner restriction of the ring-shaped cavity. It is reciprocable with respect to the wall, so that the roller members are initially able to be driven circumferentially at start-up due to sliding friction between the roller members and the radial restriction of the ring-shaped cavity.

That is, a conventional type of mass compensating mechanism of a diaphragm pump is combined with an automatic balance unit, which is exclusively produced by a gas-generated and variable force (Gas-Kraefte) or other medium. The tightened force (Mediu
m-Kraefte).

In the case of a combination of rotational and oscillating movements, the aforementioned principle for unbalance compensation is additionally used for a rigidly mounted co-rotating compensating mass. Therefore, in the present invention, a principle for unbalance compensation using a roller member circulating in a ring-shaped hollow chamber in a diaphragm pump is used. The changing forces are almost automatically compensated. Since the mass required for mass compensation of the eccentric or crankshaft and the connecting rod or the like is rigidly mounted, only a relatively small mass is used for automatic compensation of changing or opposing forces. Absent. Correspondingly, the roller elements can be small and light, so that they begin to move in the ring-shaped cavity with already small imbalances or opposing forces to be compensated, to reach the position of the optimum mass compensation. Thus, particularly accurate and fine mass compensation is achieved, because not all the dynamic forces are compensated via the above-mentioned principle, but only the forces generated by the ejection medium, and thus unbalance and vibration. Only the roller member compensates.

Since the interior of the ring-shaped hollow chamber is empty and free of liquid except for the roller members, there is a correspondingly small resistance to the rolling of the roller members and, therefore, to the changing forces of the roller members. Reacts finely and quickly to Although automatic balancing devices for placing the roller members together with oil in the cavity are known, this forms a correspondingly inertial mechanism, since the resistance of the liquid must be overcome. Yes, as a result, the balancing device is not suitable for quickly compensating for the changing forces produced by the gas.

It is important that the radial width of the ring-shaped cavity be slightly larger than the diameter of the roller member. At the first moment, i.e. at start-up, rather than the rolling process first taking place, a sliding friction occurs and the roller members exert a druckkraft on each other. Thus, one roller element located in the lower region of the hollow space pushes the roller element adjacent to said roller element on the basis of friction and mass inertia, and also lifts up in the radial direction, so that the roller element is located in the hollow area. Connect to the inside. The radial dimension of the cavity only slightly exceeds the radial dimension of the roller element, so that there is a correspondingly slight recoil of the roller element radially inward.
Reaktions are sufficient, so that the roller members are entirely entrained in frictional forces in the direction of rotation and are therefore freely distributed around the cavity in response to the resulting imbalance. When the machine (diaphragm pump) reaches operating speed, the imbalance is based on a rigidly mounted mass compensating element and the roller elements are held by centrifugal force on the running path outside the cavity, ie on the wall located radially outside. Being small enough to exercise. The roller members then roll in response to the change in the imbalance, since the roller members have a small distance to the wall of the cavity. Correspondingly, the resistance in the opposite direction to the roller movement is small, since the cavity is not filled with liquid, so that the automatic compensation of the imbalance due to changes and vibrations caused by different opposing forces. Is performed very sensitively and quickly with high accuracy. The combination of the arrangements according to the invention allows precise and fine compensation of vibrations caused by different gas forces.

In effect, despite the fact that the roller elements are kept at the deepest points of the running track on the basis of low friction on the running track and on the basis of weight, even when the diaphragm pump is started without the liquid filling of the hollow body, Will be taken.
This is particularly the case when the axis of rotation for the housing forming the ring-shaped cavity is arranged horizontally in the use position. The aforementioned displacement (Gedraenge) of the roller elements in a slightly larger cavity results in a certain mutual clamping (Verklemmung), whereby the roller elements are entrained on starting.

Preferably, the ring-shaped cavity is formed as a circular groove, the open side of which is closed by a removable cover. This simplifies the assembly and, in particular, the mounting of the roller elements in the grooves. A ring-shaped cavity is, on the one hand, very simple and, on the other hand, can be produced very precisely. Importantly, the movement of the roller members is subject to as little resistance as possible, so that a correspondingly precise roller trajectory (running trajectory) is advantageous,
In this case, the roller tracks and the roller members may be hardened in order to minimize the resistance.

[0013] The radial width of the annular cavity reduces the maximum diameter of the roller element by approximately 1/2 to 2 percent, preferably by approximately 1 to 1 1/2 percent, and especially by a tenth of a millimeter to approximately four percent. Exceeded by less than a fraction of a millimeter.

The outer wall, which serves as a roller track for the cavity, extends parallel and linearly to the axis of rotation in cross section (plane in FIG. 3) to form a hollow cylinder. . Such a hollow cylinder can be manufactured in a particularly simple manner, since no undercut is formed, for example, in the case of a substantially convex surface on the wall or running track of the hollow chamber. Further, the filling of the roller member is facilitated.

It is particularly advantageous if the wall arranged on the small diameter of the cavity is linearly arranged in the same manner as the outer wall,
And it is formed parallel to the wall located outside.
The roller members can be precisely aligned over the entire circumference of the cavity and at the axially constant radial distance of the restriction of the cavity, and the filling, replacement or refilling of the roller members is simple.

In a preferred embodiment, the roller element is a sphere. The spheres are manufactured extremely precisely and precisely and are trapped during operation in a ring-shaped cavity (Verkantun).
Good circulation without fear of On the other hand, during the first start-up, the catch serves, according to the selected dimensional conditions, for distributing the spheres in the cavity.

Advantageously for the mass compensation, and for the initial start-up and initially a short time to the desired engagement, at least three or four of the same dimensions and in particular the same mass,
In particular, five roller members or balls are arranged in a ring-shaped hollow chamber. This allows for a fine compensation of the changing forces generated by the gas, especially in diaphragm pumps which perform a vertically directed movement using a connecting rod, which advantageously increases the resistance. Such a liquid is not provided in the ring-shaped hollow chamber.

[0018]

DETAILED DESCRIPTION OF THE INVENTION A diaphragm pump, shown in FIG. 1 at 1 and having a stroke piston 2 in a known manner, is fitted with a diaphragm 4 clamped in a casing 3 in a known manner. Have been. A connecting rod 5 is applied to the stroke piston 2, and the connecting rod itself is driven by an eccentric 6 (see FIG. 3) at an end opposite to the stroke piston 2. A crank may be provided instead of the eccentric body 6. At least a part of the rotating and oscillating mass is compensated by a fixed, synchronously driven counterweight 7.

As is clear from FIGS. 1 and 3, a ring-shaped hollow chamber 9 is arranged in a rotating casing 10 concentrically with respect to a rotation axis 8, and the casing is
It is movably supported on a shaft 11 having an eccentric 6.
A plurality of roller members 12 are arranged in the ring-shaped hollow chamber 9, and the roller members can freely roll along an inner surface 13 of the outer periphery of the hollow chamber 9, which is also referred to as an outer surface 13 below.

As can be seen from FIG. 3, the rotating casing 10 is arranged at the free end of the shaft 11 adjacent to the eccentric 6 and the bearing of the connecting rod 5 to the eccentric. A bearing for the shaft 11, in this embodiment a rolling bearing 14, is provided on the side opposite to the casing 10.

As is evident from the drawing, the ring-shaped hollow space 9 is formed as a circular groove, which is closed on its open side by a removable cover 15. The radial width of the ring-shaped cavity 9 corresponds approximately to the largest diameter of the roller element 12, but slightly exceeds it in the drawing. For example,
The radial width of the ring-shaped cavity 9 exceeds the maximum diameter of the roller member 12 by approximately 0.5 to 2%, preferably 1 to 1.5% of the diameter. The value of the width of the groove forming the ring-shaped hollow space 9 exceeding the diameter of the roller member is actually less than one tenth to one quarter millimeter.

Therefore, when the operation of the diaphragm pump 1 is started, first, all the roller members 12 arranged at the deepest portion of the ring-shaped hollow chamber 9 based on FIG. It is swung left and right, i.e. does not perform a rotational movement corresponding to the rolling, since the roller members alternately contact the inner surface 16 and the outer surface 13 of the ring-shaped cavity 9. . Thus, sliding friction occurs during the start-up phase (Anlauf-Phase), so that the roller members 12 are more or less evenly distributed around the cavity 9.

FIG. 4 schematically shows the starting process. The diaphragm 1 and, consequently, the casing 10 have an arrow P
When the engine is started in the direction of f1, the roller member 12 or the ball contacting the deepest portion of the outer surface 13 of the ring-shaped hollow chamber 9 is counter-rotated by friction as shown by an arrow Pf2. However, while this applies to both roller members 12 located on the outside, the roller members 12a located between the roller members are based on the friction against the roller members 12 that contact the roller members 12a on both sides. 12 is rotated in a different direction from that of the rotation of T12, which is indicated by the arrow Pf3. Due to the rotation of the roller member 12a located therebetween, the roller member 12a simultaneously comes into contact with the roller member 12a.
2 and thus come into contact with the inner surface 16 of the grooved cavity 9, so that the roller members 12, 12a are clamped together in the cavity 9, whereby the entire roller member 12 is shown in FIGS. During the subsequent course, the gravity and the dynamic force of the starting course (Dynami
According to k), they are separated from each other, and are entrained in the rotational direction until they occupy a predetermined position in the groove-shaped hollow chamber 9 according to the imbalance. FIG. 5 shows the three roller members 12 shown in FIG.
Only two of them are shown, since the third roller member is separated from the roller member 12 visible in FIG. 5 by a correspondingly large distance. The roller member 12 is held on the basis of centrifugal force, and therefore occupies the required position according to the imbalance.

When the operating speed is reached, the roller member 12
Are distributed as shown in FIGS. 2 and 5 and roll into their respective positions very finely in the event of a small change in the gas (Gaskraft) generated by the gas evolved and the resulting imbalance. The unbalance is then automatically compensated for, because the roller members contact the outer surface 13 of the cavity 9 due to centrifugal force and no longer have a cavity 9 due to a slightly smaller diameter relative to the width of the cavity 9. Is not in contact with the inner surface 6, i.e. the rolling movement of the roller members is no longer damped.

Advantageously, the interior of the ring-shaped hollow space 9 is empty except for the roller members 12 and contains no liquid, of course apart from normal atmospheric air. Therefore, it is not necessary to entrain a relatively inert liquid portion when the position of the roller member 12 changes due to the changing force and the resulting imbalance. Therefore, the whole mechanism
Responding accurately and quickly to changing forces, the constant mass force is essentially compensated for by the counterweight 7 from the beginning, i.e. only the changing additional small forces need to be taken into account. . Errors in the counterweight 7 may additionally be compensated.

As is evident from FIG. 3, the outer surface 13, which serves as a roller track for the hollow space 9, ie the outer wall, is arranged in an axially parallel and linear fashion in cross section, That is, the large-diameter wall (outer surface 13) of the ring-shaped hollow chamber 9 forms a hollow cylinder. The inner wall (inner surface 16) arranged at the smaller diameter of the cavity 9 is also linear in the same manner as the outer wall (outer surface 13) and parallel to the outer wall (outer surface 13). Is composed of
As a result, the radial width of the ring-shaped hollow chamber 9 is maintained uniformly in the axial direction. Therefore, the roller member 12 can be fitted into the hollow chamber 9 without any special filling opening without any problem with the cover 15 opened. Since the roller members 12 are preferably spherical, there is no danger of tilting during operation as occurs with cylindrical roller members.

In the exemplary embodiment, five spherical roller members 12 are arranged in a ring-shaped hollow space 9, all of which have the same dimensions and the same mass, in which case, May be provided with fewer or more spheres.

The axis of rotation 8 of the casing 10 forming the ring-shaped hollow chamber 9 is arranged horizontally as shown in FIG. 3, and the connecting rod 5 is substantially vertical as shown in FIG. Is turned. It is also possible to arrange the connecting rod 5 horizontally at the use position with the rotation axis 8 being horizontal. The axis of rotation 8 may extend vertically in the use position.

Advantageously, the counterweight 7, which is fixedly mounted, is arranged on the housing 10, so that the housing 10 has an additional function. The counterweight (opposing weight) 7 is, of course, oriented opposite to the eccentric direction of the eccentric body 6 and the direction of the connecting rod 5, that is to say it is arranged at the deepest point at the starting position in FIG. In the diaphragm pump, the unbalance is reduced at all revolutions based on the immovable mass compensation using the counterweight 7, and the roller member 12 or the ball freely rolls along the outer wall 13 by centrifugal force. Dynamic movement, in which case the resistance is significantly lower,
A mass compensation that allows quick and accurate self-adjustment of the changing forces generated by the operating gas is possible, while at the same time the construction costs are relatively low. Undesirable vibrations due to the changing forces generated by the medium or gas are avoided or almost avoided.

The stroke piston 2 of the diaphragm pump 1 is operated by means of the connecting rod 5 to move the diaphragm 4 mounted on the stroke piston and clamped in the pump casing 3. The connecting rod 5 itself is a stroke piston 2
The load is driven by the eccentric body 6 or the crank portion of the drive shaft 11 at the end opposite to the above. In this case, at least a part of the rotating mass of the oscillating mass is compensated by at least one counterweight 7 which is rigidly mounted and moves synchronously with the oscillating mass. The co-rotating casing 10 for automatic compensation of changing imbalances based on the changing forces generated by the gas or medium.
Roller member 1 disposed in a ring-shaped empty cavity 9 formed in casing 10 coaxially with respect to the rotation axis of
2. Advantageously, the sphere is free to roll along the inner surface 13 of the outer periphery of the cavity 9, ie the outermost wall, so that it begins to move with a small unbalance already, so that an optimal mass compensation To the point where you do.

[Brief description of the drawings]

FIG. 1 is a vertical sectional view of a diaphragm pump in a stationary state.

FIG. 2 is a vertical sectional view of the diaphragm pump in an operating state.

FIG. 3 is a vertical sectional view of the diaphragm pump at a position rotated by 90 ° with respect to the positions of FIGS. 1 and 2;

FIG. 4 is an enlarged schematic view of three roller members or balls in contact with each other during starting of the diaphragm pump.

FIG. 5 is an enlarged schematic view of a roller member or ball during normal operation of the diaphragm pump, ie after a first start-up phase, after the distribution of the ball or roller member in the hollow chamber during said start-up phase;

[Explanation of symbols]

1 diaphragm pump, 2 stroke piston,
3 casing, 4 diaphragm, 5 connecting rod,
6 eccentric body, 7 counterweight, 8 axis of rotation,
9 hollow chamber, 10 casing, 11 shaft,
12 roller members, 13 inner surface, 14 rolling bearing, 15 cover, 16 inner surface

Claims (10)

(57) [Claims] At least one diaphragm (4) and a stroke piston (2) mounted on said diaphragm (1)
Diaphragm pump (1) having a connecting rod (5) engaged with a stroke piston, the connecting rod being loaded by an eccentric (6) or a crankshaft at the end opposite to the stroke piston (2). At least a portion of the rotating mass of the oscillating mass has at least one counterweight disposed opposite the oscillating mass and rigidly attached to the oscillating mass and moving synchronously with the oscillating mass. 7)
Or an eccentric (6) or a rotational axis of the crankshaft (8) in the form compensated by mass
A ring-shaped cavity (9) is coaxially arranged in the casing (10) or casing part which rotates together and has at least two roller members (12) in the cavity.
The roller member rolls freely on the inner surface (13) of the outer peripheral portion of the hollow chamber (9), and the inside of the ring-shaped hollow chamber (9) is ), Except that the ring-shaped hollow chamber (9) has a radial width slightly larger than the radial diameter of the roller member (12). ) Can reciprocate between the outer limiting part or wall and the inner limiting part or wall of the ring-shaped hollow space (9) by imbalance at the time of starting, whereby the roller member (12)
A diaphragm with at least one stroke piston, characterized in that it can be initially entrained in the circumferential direction at the time of starting on the basis of sliding friction between the roller members and the radial restriction of the ring-shaped hollow space (9). pump. 2. The diaphragm pump according to claim 1, wherein the ring-shaped hollow space is formed as a circular groove, the open side of which is closed by a removable cover. 3. The diaphragm pump as claimed in claim 1, wherein the radial width of the ring-shaped cavity (9) exceeds the maximum diameter of the roller member (12) by approximately 乃至 to 2%. 4. The radial width of the ring-shaped cavity (9) exceeds the maximum diameter of the roller member (12) by a value of less than one tenth of a millimeter to approximately one-quarter of a millimeter. 3. The diaphragm pump according to 1 or 2. 5. The method as claimed in claim 1, wherein the outer wall (13) serving as a roller track for the hollow space (9) extends linearly in cross section and forms a hollow cylinder. The diaphragm pump according to claim 1. 6. The wall (16) arranged at the small diameter of the cavity (9) is linearly and in the same manner as the outer wall (13) with respect to the outer wall (13). 6. The diaphragm pump according to claim 5, wherein the diaphragm pump is formed in parallel. 7. The diaphragm pump according to claim 1, wherein the roller member (12) is a sphere. 8. At least three or four or five roller members (1) having the same dimensions and in particular the same mass.
2) The diaphragm pump according to claim 1, wherein the sphere is arranged in a ring-shaped hollow chamber (9). 9. The method according to claim 1, wherein the axis of rotation for the housing defining the annular cavity is arranged horizontally in the position of use. Diaphragm pump. 10. An opposed weight (7), which is rigidly mounted, is arranged on the casing (10) and is arranged on the side opposite to the eccentric part of the eccentric (6) and / or the connecting rod (5). The diaphragm pump according to any one of claims 1 to 9.